US8459661B2 - Wheel suspension for motor vehicles - Google Patents

Wheel suspension for motor vehicles Download PDF

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Publication number
US8459661B2
US8459661B2 US12/565,389 US56538909A US8459661B2 US 8459661 B2 US8459661 B2 US 8459661B2 US 56538909 A US56538909 A US 56538909A US 8459661 B2 US8459661 B2 US 8459661B2
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United States
Prior art keywords
wheel
axle
support member
wheel suspension
pivoted
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Active, expires
Application number
US12/565,389
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English (en)
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US20100072714A1 (en
Inventor
Wolfgang Schmid
Karl-Heinz Meitinger
Wilfried Michel
Christoph Kossira
Hugo Mueller
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Audi AG
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Audi AG
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Publication date
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Assigned to AUDI AG reassignment AUDI AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KOSSIRA, CHRISTOPH, MEITINGER, KARL-HEINZ, MUELLER, HUGO, SCHMID, WOLFGANG, MICHEL, WILFRIED
Publication of US20100072714A1 publication Critical patent/US20100072714A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D17/00—Means on vehicles for adjusting camber, castor, or toe-in
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G7/00—Pivoted suspension arms; Accessories thereof
    • B60G7/006—Attaching arms to sprung or unsprung part of vehicle, characterised by comprising attachment means controlled by an external actuator, e.g. a fluid or electrical motor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G7/00—Pivoted suspension arms; Accessories thereof
    • B60G7/008—Attaching arms to unsprung part of vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D9/00—Steering deflectable wheels not otherwise provided for
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2200/00—Indexing codes relating to suspension types
    • B60G2200/10—Independent suspensions
    • B60G2200/14—Independent suspensions with lateral arms
    • B60G2200/144—Independent suspensions with lateral arms with two lateral arms forming a parallelogram
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2200/00—Indexing codes relating to suspension types
    • B60G2200/40—Indexing codes relating to the wheels in the suspensions
    • B60G2200/46—Indexing codes relating to the wheels in the suspensions camber angle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2200/00—Indexing codes relating to suspension types
    • B60G2200/40—Indexing codes relating to the wheels in the suspensions
    • B60G2200/462—Toe-in/out
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/418—Bearings, e.g. ball or roller bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/419—Gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/42—Joints with cam surfaces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/44—Centering or positioning means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
    • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
    • B60G2206/50—Constructional features of wheel supports or knuckles, e.g. steering knuckles, spindle attachments

Definitions

  • the invention relates to a wheel suspension for motor vehicles.
  • the camber or track of the wheels can be set by way of an actuator so that by controlling the actuator the driving behavior of the motor vehicle can be actively influenced.
  • the wheel carrier of the wheel suspension has a wheel-side support member which pivotally supports the vehicle wheel, and an axle-side support member, between which an actuator is connected as an intermediate element.
  • the actuator is a hydraulic actuating cylinder here which is supported on the one hand on a bearing bracket of the wheel carrier and on the other hand with its piston rod it presses against the external anti-friction bearing race of a wheel bearing, as a result of which the wheel bearing together with the vehicle wheel executes a pivoting motion around a hinge center in order to change the toe-in or toe-out angle or the camber angle of the pertinent vehicle wheel.
  • the arrangement of the actuator known from DE 39 28 135 A1 between the bearing bracket and the wheel bearing is mechanically complex and takes up a large amount of installation space, with correspondingly high weight.
  • the overall high weight of the wheel suspension is especially disadvantageous since the wheel carrier is an unsprung mass.
  • the bearings provided between the support members and the intermediate element in the bearing sites are configured such that they can accommodate not only axial compression forces, but also axial tensile forces and radial forces. Bearings designed in this way have unduly large installation volumes under the limited installation space conditions in the region of the wheel carrier.
  • the object of the invention consists in making available a wheel suspension with an active steering system which is located in the wheel suspension in a manner which is mechanically simple and favorable to installation space.
  • the wheel suspension has a pretensioning means which presses the wheel-side support member and the axle-side support member with a pretensioning force into contact with one another.
  • the bearing sites in the wheel suspension are exposed only to axial compressive forces and radial forces by the bracing of the two support members. Axial tensile forces are conversely accommodated by the pretensioning means itself. In this way, in the wheel suspension according to the invention simple axial bearings with correspondingly reduced installation space can be used.
  • the support members and the intermediate element in the direction of action of the pretensioning force are connected to one another in a plug connection without an undercutting structure being necessary for axial fixing of the support members and intermediate elements.
  • the support members and intermediate elements can therefore be easily plugged into one another during assembly.
  • the pretensioning means is connected between the two support members and connects them to one another.
  • the pretensioning means is preferably located radially outside the intermediate element and is functionally decoupled from it.
  • the pretensioning means is designed as a coupling which is connected between the wheel-side support member and the axle-side support member.
  • the coupling as a torque bridge can transfer the torque, for example, a braking moment, from the wheel-side support member to the axle-side support member and thus to the vehicle body. In this way, with the additional coupling a further path of forces and moments, in addition to the intermediate element, is made available via which the braking moment can be reliably transmitted to the vehicle body.
  • the pretensioning means can preferably be functionally completely decoupled from the intermediate element or actuator or its pivoted parts connected between the support members. In this way neither the pretensioning means nor the actuator is functionally influenced by the respectively other component.
  • the pretensioning means can be a universal joint which is connected between the wheel-side and axle-side support member.
  • the universal joint can have an articulated part, such as a ring element which is located preferably radially outside the intermediate element and which extends with a radial distance around the intermediate element.
  • the universal joint can have bridges which are connected to the support members and which in the form of an articulated fork in turn are articulated to the ring element by way of axes of rotation. In this way, torsionally stiff and play-free torque transmission between the two support members of the wheel carrier takes place by means of a universal joint.
  • the intermediate element can be an actuator with a wheel-side pivoted part and an axle-side pivoted part which are mounted between the wheel-side support member and the axle-side support member and are rotatable to one another around their axes of rotation.
  • the wheel-side pivoted part can be deflected relative to the axle-side pivoted part by turning the two pivoted parts by the swivel angle to one another. Accordingly, the vehicle wheel provided on the wheel-side support member therefore is also swiveled by a camber angle or track angle.
  • the wheel-side pivoted part with its middle axle can be moved in the manner of wobbling motion around its axis of rotation.
  • the axis of rotation of the wheel-side pivoted part can be tilted by an angle relative to the axis of rotation of the axle-side pivoted part.
  • the two pivoted parts can be in contact, preferably in rolling contact, by way of bearing sites which lie in turn in one plane of rotation.
  • the plane of rotation is aligned perpendicular to the axis of rotation of the wheel-side pivoted part.
  • the wheel-side pivoted part with the pertinent wheel-side support member for the vehicle wheel can move in wobbling motion around its axis of rotation.
  • the swivel angle between the wheel-side pivoted part and the axle-side pivoted part changes as a function of the angle of rotation of the wheel-side pivoted part.
  • the three-dimensional alignment of the angle arrangement formed by the two pivoted parts can be changed by rotation of the axle-side pivoted part which takes place simultaneously or offset in time relative to the axle-side support member.
  • the two pivoted parts can be arranged internested into one another.
  • one of the two pivoted parts for example the wheel-side pivoted part, can be designed as a cup-shaped hollow profile part, in which there is an axle-side pivoted part.
  • the bottom of the cup-shaped pivoted part in this case can be designed as a tilted control surface which is in contact with the control surface of the axle-side pivoted part.
  • the two pivoted parts can be designed as hollow cylinders. Their cylindrical interior can be used as the installation space for the actuating drives.
  • an articulated shaft for driving the vehicle wheel can be routed through the interior of the pivoted parts.
  • actuating drives within the hollow cylindrical pivoted parts is especially preferred when the vehicle wheel is trailed, that is to say, is not driven by an articulated shaft.
  • the cavity of the pivoted parts is empty. Accordingly, actuating drives can be easily located in it.
  • the aforementioned wheel-side and axle-side bridges of the universal joint with the formation of clear spaces are preferably located angularly offset to one another.
  • an actuating drive can be located in these clear spaces in a manner favorable to installation space or, alternatively, there can be a gearing stage located on the outside on the pivoted part.
  • the middle of the universal joint according to one version of the invention lies at the height of the instantaneous center of rotation of the wheel carrier, as a result of which a change in length does not occur when the wheel carrier is adjusted.
  • FIG. 1 shows in a schematic a wheel suspension on the rear axle of a vehicle according to the first embodiment
  • FIG. 2 shows in an enlarged schematic partial sectional view the wheel suspension in isolation
  • FIG. 3 shows a view of the wheel suspension which illustrates the swiveling motions of the two pivoted parts for setting the track angle or camber angle;
  • FIG. 4 shows the wheel suspension in an exploded representation
  • FIG. 5 shows the wheel suspension according to the second embodiment with an integrated universal joint
  • FIG. 6 shows the wheel suspension according to the third embodiment.
  • FIG. 1 shows a wheel suspension in conjunction with a known suspension arm axle in which a wheel carrier 3 which bears the vehicle wheel 1 among other things using an upper suspension arm 5 and a lower suspension arm 7 are pivotally coupled to the vehicle body 11 by way of body-side steering bearings 9 .
  • the body-side steering bearings 9 and the wheel carrier-side steering bearings 13 are of conventional design.
  • a support spring 15 with an assigned McPherson strut unit is moreover supported in the conventional manner.
  • the wheel carrier 3 can be combined with any axle, for example a rigid axle, a compound steering axle, a multi-steering axle, etc.
  • the wheel carrier 3 has a wheel-side support member 17 and an axle-side support member 19 .
  • the vehicle wheel 1 is supported by way of a wheel hub in a wheel bearing of the wheel-side support member 17 , which bearing is not shown.
  • the brake system can be mounted in the conventional manner on the wheel-side support member 17 .
  • the two suspension arms 5 , 7 are coupled to the axle-side support member 19 by way of steering bearings 13 .
  • an actuator 21 which has a wheel-side pivoted part 23 and an axle-side pivoted part 25 .
  • the two pivoted parts 23 and 25 are in contact with one another on their tilted control sides with the interposition of axial bearings 24 .
  • a central ring flange 36 is molded on the control side of the pivoted part 23 .
  • the ring flange 36 projects through a mounting opening in the opposite control side of the axle-side pivoted part 25 .
  • a radial bearing 26 Between the ring flange 36 and the opening edge of the axle-side pivoted part 25 there is a radial bearing 26 .
  • the pivoted parts 23 , 25 are likewise supported on their end sides facing away from the control sides by way of radial bearings 26 on axial projections 31 of the support members 17 , 19 which each project into the hollow space of the pivoted parts 23 , 25 .
  • the pivoted parts 23 , 25 as shown in FIG. 3 are supported between the two support members 17 , 19 to be able to rotate respectively around their axes of rotation 27 , 28 .
  • the axis 28 of rotation of the pivoted part 25 is axially aligned in the transverse direction of the vehicle y and coaxially to the middle axis 29 of the pivoted part 23 .
  • the axis of rotation 27 of the pivoted part 23 is tilted up by an angle of incline ⁇ .
  • For rotary driving of the pivoted part 23 by an angle ⁇ of rotation the pivoted part 23 moves with its middle axis 29 in wobble motion with a variable swivel angle ⁇ around the axis 27 of rotation.
  • the camber angle ⁇ is 0 in the illustrated yz plane of the vehicle wheel 1 .
  • the pivoted part 23 with its middle axle 29 ′ is moved up in wobbling motion around the axis 27 of rotation. This yields a swivel angle ⁇ between the two pivoted parts 23 and 25 .
  • the vehicle wheel 1 or the wheel-side support member 17 is also swiveled around the camber angle ⁇ in the yz plane.
  • the pivoted part 25 can also be turned by an angle ⁇ of rotation relative to the axle-side support member 19 .
  • the pivoted part 23 which is shown in FIG. 3 and which is bent relative to the axle-side pivoted part 25 is swiveled out of the yz plane, by which the track angle ⁇ of the vehicle wheel 1 can be set.
  • the pivoted part 23 With sole rotation of the pivoted part 23 by an angle of rotation ⁇ the pivoted part 23 can swivel out of the yz plane.
  • FIG. 4 shows the wheel suspension of FIG. 2 in an exploded representation in order to illustrate the assembly of the wheel suspension.
  • the wheel-side support member 17 with its axle projection 31 is inserted into the open end side of the pivoted part 23 with the interposition of the radial and axial bearings 24 , 26 which are not shown here.
  • the ring flange 36 which is provided on the control side of the pivoted part 23 is likewise inserted in the axial direction into the corresponding mounting opening of the pivoted part 25 .
  • the support member 19 with its axle projection 31 is inserted into the cavity of the pivoted part 25 , likewise with the interposition of radial and axial bearings 24 , 26 .
  • the components of the wheel suspension can therefore be easily mounted in terms of mounting technology in a plug-in connection without an undercut which acts in the axial direction being necessary at the connecting sites.
  • an additional pretensioning means 57 which is shown in FIG. 2 only by the broken line.
  • the pretensioning means 57 in the axial direction applies a pretensioning force F V to the support members 17 , 19 with the interposed pivoted parts 23 , 25 .
  • the pretensioning means 57 is completely decoupled in functional terms from the intermediate member 21 and effects axial fixing of the components of the wheel suspension. Coupling of the support members 17 , 19 to the pivoted parts 23 , 25 or coupling between the two pivoted parts 23 , 25 by a complex undercutting construction is thus avoided.
  • the bearing sites should be designed not only for compressive, but also for tensile loads.
  • Bearings designed in this way are, for example, preloaded bearing pairs in a X or O arrangement with tapered roller bearings.
  • Such double-row bearing combinations due to twice the number of bearings in the direction of installation depth must be dimensioned to be large; this is disadvantageous in view of the limited installation space conditions in the wheel suspension.
  • torque motors 38 , 39 which mesh with the internal toothing of the respective pivoted part 23 by way of a gear train 40 .
  • the setpoints ⁇ setpoint and ⁇ setpoint are computed for the track and camber angles by a higher-order control device which is not shown based on different vehicle parameters and are routed to a control means 49 .
  • the control means 49 can be triggered by way of signal lines 50 with the torque motors 38 , 39 of the two pivoted parts 23 , 25 which turn the respective pivoted parts 23 , 25 over an angle of rotation ⁇ or an angle of rotation ⁇ .
  • phase-angle sensors 51 are assigned to the two pivoted parts 23 , 25 , detect one actual value ⁇ actual and ⁇ actual of the two pivoted parts 23 , 25 at a time and feed them back to the control means 49 .
  • the pretensioning means is designed as a universal joint 57 which is connected between the wheel-side support member 17 and the axle-side support member 19 .
  • FIG. 5 in fundamental structure matches the preceding embodiment. In this respect, reference is made to its description.
  • the vehicle wheel 1 which is held on the wheel-side support member 17 is not trailed, i.e., is not driven by an articulated shaft, but there is additionally an articulated shaft 58 which is shown by the broken line in FIG. 5 .
  • the articulated shaft 58 is routed through the cavities 35 of the two pivoted parts 23 , 25 and drives the vehicle wheel 1 , as is the case for a rear wheel or all wheel drive.
  • the two actuating drives 38 , 39 (in FIG. 5 only the actuating drive 39 is shown) are no longer located within the cavities 35 , but outside the cavity 35 of the two pivoted parts 23 , 25 .
  • the two actuating drives 38 , 39 as shown in FIG. 5 are in a toothed connection by way of spur pinion stages 73 which are provided on the outer peripheral side on the pivoted parts 23 , 25 .
  • the universal joint 57 here is not only a pretensioning means which presses the support members 17 , 19 into contact with one another with a pretensioning force F V .
  • the universal joint 57 acts additionally as a torque bridge via which, for example, a braking moment is transmitted from the wheel-side support member 17 to the axle-side support member 19 .
  • the universal joint 57 as shown in FIG. 5 as the central articulated part has a gimbal 63 which are shown in a half section and which extend radially outside around the pivoted parts 23 , 25 and are spaced apart from the pivoted parts 23 , 25 over a radial distance a.
  • the gimbal 63 are connected by way of a universal joint fork 77 to the wheel-side support member 17 and to the axle-side support member 19 .
  • FIG. 6 shows a technical implementation of the wheel suspension shown in FIG. 5 .
  • the structure and the method of operation of the wheel suspensions shown in FIGS. 5 and 6 are essentially the same.
  • the wheel suspension shown in FIG. 6 likewise has two wheel-side and axle-side support members 17 , 19 .
  • the wheel-side support member 17 is inserted with the central axle projection 31 into the hub section 78 of the wheel-side pivoted part 23 .
  • the hub section 78 is spaced radially apart from the cylindrical outside wall 79 of the pivoted part 23 by way of an annular gap.
  • the hollow cylindrical pivoted part 25 whose tilted end side is in contact with the corresponding gap base of the pivoted part 23 by way of the axial needle bearing 24 projects into the annular gap between the cylindrical outside wall 79 and the hub section 78 .
  • the pivoted part 25 with its inside periphery sits on a hub section 81 of the axle-side support member 19 with the interposition of a radial needle bearing 26 .
  • other contact surfaces of these pivoted parts 23 , 25 are also supported by way of axial and radial needle bearings 24 , 26 . Since according to FIG. 6 the axial needle bearings 24 are designed only for compressive stress, and not for tensile stress, they can be made with a lower overall height. Due to the reduced overall height, overlapping of individual bearings 24 , 26 can take place, as a result of which the axial installation space can be further shortened.
  • Universal joint bridges 65 , 66 each project over the pivoted parts 23 , 25 both from the wheel-side support member 17 and also from the axle-side support member 19 .
  • the bridges 65 , 66 are placed under axial pretensioning on the bearing pins 68 of the gimbal 63 , as a result of which the support members 17 , 19 are pressed into contact with a pretensioning force Fv with interposition of the two pivoted parts 23 , 25 .
  • the actuating drive for rotary adjustment of the pivoted parts 23 , 25 is not shown in FIG. 6 . It can, however, be designed analogously to the actuating drive, as is explained with reference to FIG. 5 .
US12/565,389 2008-09-23 2009-09-23 Wheel suspension for motor vehicles Active 2030-09-25 US8459661B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008048569 2008-09-23
DE102008048569A DE102008048569A1 (de) 2008-09-23 2008-09-23 Radaufhängung für Kraftfahrzeuge
DE102008048569.1 2008-09-23

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Publication Number Publication Date
US20100072714A1 US20100072714A1 (en) 2010-03-25
US8459661B2 true US8459661B2 (en) 2013-06-11

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ID=41100649

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Application Number Title Priority Date Filing Date
US12/565,389 Active 2030-09-25 US8459661B2 (en) 2008-09-23 2009-09-23 Wheel suspension for motor vehicles

Country Status (5)

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US (1) US8459661B2 (de)
EP (1) EP2342119B1 (de)
CN (1) CN102164807B (de)
DE (1) DE102008048569A1 (de)
WO (1) WO2010034368A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10351173B2 (en) * 2014-07-26 2019-07-16 Audi Ag Wheel carrier for a two-track motor vehicle

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009058490A1 (de) * 2009-12-16 2011-06-22 Audi Ag, 85057 Vorrichtung zum Verstellen von Sturz und/oder Spur der Räder von Radaufhängungen
DE102009058489A1 (de) * 2009-12-16 2011-06-22 Audi Ag, 85057 Vorrichtung zum Verstellen von Sturz und/oder Spur der Räder von Kraftfahrzeugen
DE102010007994A1 (de) * 2010-02-15 2011-08-18 Audi Ag, 85057 Radaufhängung für ein Kraftfahrzeug
DE102013008652B4 (de) * 2013-05-21 2016-10-13 Audi Ag Vorrichtung zur Sturz- und/oder Spurverstellung eines Fahrzeugrades
CN115195861B (zh) * 2022-08-12 2023-09-12 浙江极氪智能科技有限公司 前束调节装置和车辆

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3833235A (en) * 1973-06-15 1974-09-03 D Worsham Wheel camber-maintaining assembly
WO1989008566A1 (en) 1988-03-19 1989-09-21 Zahnradfabrik Friedrichshafen Ag Rigid driven steering axle
DE3928135A1 (de) 1988-08-31 1990-03-01 Volkswagen Ag Radaufhaengung fuer kraftfahrzeuge, insbesondere fuer personenkraftwagen
JPH0299469A (ja) 1988-10-05 1990-04-11 Kubota Ltd 作業車のステアリング構造
WO1996007557A1 (en) 1994-09-08 1996-03-14 Frank Victor Csik Castor-independent-steering-arm-mounting
WO1998016418A1 (en) 1996-10-11 1998-04-23 Novelty Inventions Ab Angle setting device for vehicle wheels
US20030011157A1 (en) * 2001-07-10 2003-01-16 Francis Aubarede Suspension system with a slider enabling camber
US20050236797A1 (en) * 2002-12-27 2005-10-27 Michelin Recherch Et Technique S.A. Wheel support device with three pivots, suspension device and vehicle comprising said support device
US20050280241A1 (en) * 2004-01-28 2005-12-22 Giorgio Bordini Suspended, articulated and powered front axle for work vehicle
DE102004049296A1 (de) 2004-10-09 2006-04-13 Bayerische Motoren Werke Ag In einem Radträger gelagerte Nabeneinheit für ein Rad eines zweispurigen Fahrzeugs
DE102005025039A1 (de) 2005-05-30 2006-12-14 Benteler Automobiltechnik Gmbh Radaufhängung
US20070080513A1 (en) * 2003-10-15 2007-04-12 Jurgen Osterlanger Device for modifying the wheel camber of a wheel on a motor vehicle
DE102008011367A1 (de) 2007-10-24 2009-04-30 Audi Ag Radaufhängung für Kraftfahrzeuge
EP2098386A1 (de) 2008-03-05 2009-09-09 Audi AG Stellglied für ein Radführungselement von Radaufhängungen
US20100013176A1 (en) * 2006-12-15 2010-01-21 Zf Friedrichshafen Ag Wheel suspension
US20100156057A1 (en) * 2007-05-23 2010-06-24 Societe De Technologie Michelin Motor Vehicle Wheel Mounting Comprising A Binary Actuator For Adjusting The Angular Position of The Plane of A Wheel
US20100253026A1 (en) * 2009-01-30 2010-10-07 Audi Ag Device for Adjusting the Chamber and/or Toe of the Wheels of Wheel Suspensions

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101939179A (zh) * 2008-02-07 2011-01-05 株式会社爱考斯研究 控制装置以及车辆

Patent Citations (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3833235A (en) * 1973-06-15 1974-09-03 D Worsham Wheel camber-maintaining assembly
WO1989008566A1 (en) 1988-03-19 1989-09-21 Zahnradfabrik Friedrichshafen Ag Rigid driven steering axle
DE3928135A1 (de) 1988-08-31 1990-03-01 Volkswagen Ag Radaufhaengung fuer kraftfahrzeuge, insbesondere fuer personenkraftwagen
JPH0299469A (ja) 1988-10-05 1990-04-11 Kubota Ltd 作業車のステアリング構造
WO1996007557A1 (en) 1994-09-08 1996-03-14 Frank Victor Csik Castor-independent-steering-arm-mounting
WO1998016418A1 (en) 1996-10-11 1998-04-23 Novelty Inventions Ab Angle setting device for vehicle wheels
US20030011157A1 (en) * 2001-07-10 2003-01-16 Francis Aubarede Suspension system with a slider enabling camber
US20050236797A1 (en) * 2002-12-27 2005-10-27 Michelin Recherch Et Technique S.A. Wheel support device with three pivots, suspension device and vehicle comprising said support device
US20070080513A1 (en) * 2003-10-15 2007-04-12 Jurgen Osterlanger Device for modifying the wheel camber of a wheel on a motor vehicle
US20050280241A1 (en) * 2004-01-28 2005-12-22 Giorgio Bordini Suspended, articulated and powered front axle for work vehicle
DE102004049296A1 (de) 2004-10-09 2006-04-13 Bayerische Motoren Werke Ag In einem Radträger gelagerte Nabeneinheit für ein Rad eines zweispurigen Fahrzeugs
DE102005025039A1 (de) 2005-05-30 2006-12-14 Benteler Automobiltechnik Gmbh Radaufhängung
US20100013176A1 (en) * 2006-12-15 2010-01-21 Zf Friedrichshafen Ag Wheel suspension
US20100156057A1 (en) * 2007-05-23 2010-06-24 Societe De Technologie Michelin Motor Vehicle Wheel Mounting Comprising A Binary Actuator For Adjusting The Angular Position of The Plane of A Wheel
DE102008011367A1 (de) 2007-10-24 2009-04-30 Audi Ag Radaufhängung für Kraftfahrzeuge
US20100327543A1 (en) * 2007-10-24 2010-12-30 Karl-Heinz Meitinger Wheel Suspension System for Motor Vehicles
EP2098386A1 (de) 2008-03-05 2009-09-09 Audi AG Stellglied für ein Radführungselement von Radaufhängungen
US20090223322A1 (en) * 2008-03-05 2009-09-10 Audi Ag Actuator for a wheel guiding element of wheel suspensions
US20100253026A1 (en) * 2009-01-30 2010-10-07 Audi Ag Device for Adjusting the Chamber and/or Toe of the Wheels of Wheel Suspensions

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10351173B2 (en) * 2014-07-26 2019-07-16 Audi Ag Wheel carrier for a two-track motor vehicle

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CN102164807A (zh) 2011-08-24
EP2342119A1 (de) 2011-07-13
CN102164807B (zh) 2013-06-19
US20100072714A1 (en) 2010-03-25
EP2342119B1 (de) 2012-09-19
WO2010034368A1 (de) 2010-04-01
DE102008048569A1 (de) 2010-03-25

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